Hydraulically controlled dispensing pump



Sept; 30, 1947 G. H. PALM 'HYDRAULICALLY CONTROLLED DISPEN'SING 'PUMP Filed June 16, 1.943 5 Sheets-Sheet 1 SePfl30, 1947 G.v H. PALMy 2,428,035

HYDRAULI CALLY CONTR OLLED DI SPENS ING; PUMP Sept 30, 1947 G. H. PALM y 2,428,035

HYDRAULI CALLY CONTR OLLED DI S PN S ING PUMP sept. 3o, 1947 G. H.i=A| 'M 2,428,035'

HYDRAULICALLY coNTRoLLED-DIsPENING- PUMP l` Filed Jupe 1e, 1943 v5 sheets-sheet@ 1 AIAA 'l' Ax wlw .www L IIIIIIII .w D. v ZM@ a A #n w fw.

a. H. PALM HYDRAULICALLY CONTROLLED DI SPENS ING PUMP Sept. 30, 1947 5 Sheets-Sheet 5 Filed June 16, 1943 immwwwwmwmm Patented Sept. 30, 1947 HYDRAULICALLY CONTROLLED DISPENSING PUMP George H. Palm, Chicago, Ill., 'assig'nor'to Stewart- VWarner Corporation, Chicago, Ill., a corporation of Virginia.

Application June 16, 1943, Serial'No. 491,005

14 Claims'.

My invention relates to lubricating systems and more particularly to power operated lubricating systems of the kind used in garages and service station-s to lubricate the bearing-s of automobiles and similar vehicles.

in present automotive practice it is usual to equip the chassis bearings of automobiles with lubricant receiving nipples or fittings and to lubricate these bearings by attaching the coupler of a lubricant compressor successively to the various ttings located at different points on the automobile chassis. The lubricant compressors used for this purpose are sometimes manually operated and sometimes operated by electricity or compressed air.

Most of the bearings of an automobile offer only moderate resistance to the in-low of lubricant and a lubricant pressure of 3,000 pounds per square inch is adequate to lubricate practically Aall of the bearings encountered. Occasionally, however, a stiff or tight bearing may be encountered which requires the use of pressures up to seven or eight thousand pounds per square inch `and 'it is usual to make power operated lubricating systems which are capable of providing the '7,000 or 8,000 pounds pressure necessary to lubricate such occasional bearings.

This means .that all of the parts of the lubrieating system must be made strong .enough Vto withstand this 7,000 or 8,000 pounds pressure and that an electric or air operated pump must be capable f producing these high pressures. -All of this greatly increases the expense of the lubricating system and reduces its eiiiciency by reducing the volume of lubricant discharged, since the amount of lubricant which can be discharged bya, motor operated pump capable of delivering vlubricant under 7,000.0r 8,000 pounds pressure is much less than can be discharged by a similar pump using the same size'v motor but designed to deliver lubricant under not more than 3,000 pounds pressure.

An object of my invention is to provide a new and improved lubricating system wherein the 'motor driven pumps are designed for a pressure of about 3,000 pounds per square inch, but which is provided with an automatic booster for increasingthe lubricant pressure to '7,000 or 8,000 pounds per square inch when the bearing resistance makes such a lubricant pressure necessary for proper lubrication. The lubricating system disclosed and claimed in this application is an improvement on that disclosed and claimed in my prior application, Serial No. 485,097, filed April 30,1943.k

yAnother object of my invention 4is to provide a new and Vimproved lubricating vsystem which is .simple and inexpensive .to 'install and operate and which maybe applied directly to the drums in which lubricant is commonly shipped 'so'th'at the lubricant is dispensed `from lthedrum to the bearing without coming in contact with dirt, water, or other `cor'itaminati'ng substances.

Another object of my invention Yis' 'to ,provide a new `,and improved 'lubricating jsys'tem which is particularly adapted for lubricating bearingsin which the .pressures required for adequate lubrication never exceed 3,000`pound's per square inch.

Another object-of my invention'i's to nprovide a new and improved pressure control valve,

Another object of my invention' is to provide anew and .improved reversing valve 'for reversing the direction of application'of Ithe primary actuating iiuid to `-a lubricant compressor.

Another bjfeot of my ini'fe'n'tion vis to provide a new .and `'improved y.l'iib'ric'rint compressor.

Another object of .my invention .is to provide a new-and improved lubricant compressor having a booster .as an integral part thereof.

Other objects and .advantages willbecome apparent as the description proceeds.

In the drawings:

Fig. lis a diagrammatic vrepreseht'ation of a preferred `form of lubricating system embodying my invention; 1

Fig. 2 -is a cross section through the .reversing land pressure control Valves showing the .pressure control valve in a different .position from that shown in Fig. 1; y

Fig. 3 is a view similar to Fig. 2, but showing the valveparts-in different positions;

Fig. 4 -is .alongitudinaL sectional View of the upper part of a .preferred form oi lubricant compressor and is'taken on the line 4 4 of Fig. 5;

Fig. .4A .is a longitudinal, sectional view of -the lower part of a preferred form of lubricant compressor, this viewY being taken on the same line as Fig. 4 and in .effect constituting a continuation of that figure;

Fig. l5 is a side elevation of the upper part of the compressor showninFig. 4 and is taken looking inthe direction of the arrow 5 of that gure; Y Fig. 46 .is a top plan .view of the compressor of Figs. 4 and 4A;

Fig. 7 is apartial, l'transverse section taken on the line 1 -'lof Figs. 5 and 6; y

Fig. 8 is a View similar to Fig. 4, but showing a modified for-moi vmy invention. The lower portion .of this modified form of my invention may be identical with .that shown in Fig. 4A.

Fig 9 is a side elevation of the upper part of the modification shown in Fig. 8 and is taken looking in the direction of the arrow 9 oi that gure; and

Fig. 10 is a top plan view of the modification of Fig. 8.

The diagrammatic representation constituting Fig. 1 ofthe drawings is intended merely to indicate a typical installation embodying my invention and is not to be construed as meaning that my invention is limited to the particular primary pumping means shown in this figure. In the embodiment of my invention represented by this gure, an electric motor 26 drives a gear pump or any other suitable type of pump 22 through a flexible coupling 24.

The pump 22 is supplied with a primary iluid, such as a light turbine oil, or any other suitable liquid, from a reservoir 26 which may be located in unitary relationship to the pump and motor, as shown, or may be placed in any other suitable position. The particular arrangement of the pump, reservoir and motor illustrated in Fig. 1 merely forms a convenient unitary assembly which can be positioned in any desired location in a garage or service station.

The primary fluid discharged by the pump 22 flows through a pipe 28 to the inlet 36 of a casting 32 having associated therewith both a lubricant pressure operated bypass valve for the primary luid and a reversing valve for reversing the direction of flow of the primary fluid to and from the lubricant compressor indicated generally by reference character 34.

Referring to Figs. 4 and 5, it will be seen that the compressor 34 has a head 36 of cast iron, or `other suitable material, terminating at its lower end in a ange 38 provided with screws 40 for attachment to a cover 42 (Fig 1), having a size suitable for closing the upper end of a lubricant drum 44. When the compressor is applied to a lubricant drum, as shown in Fig. 1, the lower or inlet end of the compressor is located just above the bottom of the drum. The compressor 34 discharges lubricant through a, hose 46 leading to a control valve 48 provided with a coupler 56 for temporary attachment to a lubricant fitting or nipple permanently mounted on a chassis bearing of an automobile or other vehicle. The control valve 48 may be of the type disclosed and claimed in my co-pending application, Serial No. 454,667, filed August 13, 1942, now Patent No. 2,380,608, dated July 31, 1945.

In addition to the head or casting 36, the compressor comprises a sleeve 52 which connects the head 36 with a second casting 54 (Fig. 4A) adapted to be located well down into the drum 44 and carrying a cylindrical extension 56 which forms the lubricant inlet for the compressor. The extension 56 has openings 58 in its side walls adjacent the lower end thereof and lubricant entering these openings is fed upwardly past an inlet check valve 66 by a feeder 62 comprising an annular washer having a loose t in the extensions 56 and mounted on a reciprocating rod 64 attached to the lower end of a tube 66. Y

The check valve 60 is located in the lower end of the casting 54V and is guided. therein by a triangular member 68 which limits lateral movement of the valve 66. The rod 64 extends through the valve 66 and member 66 and is secured to the lower end of a valve housing 'I6 by a split ring 'i2 and tubular nut V'|4. The valve housing I6 contains a ball valve 16 having a valve seat 18.

Upward movement of the Aballva'lve 16 fromthis seat 18 is-limitedby lngers86-providedby the lower end of a union 82 which connects the valve housing I6 with the lower end of tube 66.

The valve housing 16, union 82, lower end of tube 66 and upper end of rod 64 are located in and reciprocable lengthwise of a lower pumping chamber 84 formed partly by the casting 54 and partly by a tubular member 86 whose lower end is threadedly attached to this casting. The upper end of the tubular member 86 is closed by a sleeve 88 surrounding the tube 66 and forming an abutment against which packing rings 96 are urged by washer 92 and spring 94. The spring 94 rests upon a metal annulus 96 supported on a shoulder 68 provided by tubular member 86. The function of the packing rings 96 is to prevent escape of lubricant between the upper end of the tubular member 86 and tube 66 as the latter reciprocates in a manner hereinafter described.

A double acting piston |66 is aiixed to an intermediate portion of the tube 66. This piston reciprccates within a, cylinder |62 whose upper end is threaded into the head 36. Downward movement of piston |66 and tube 66 is limited by engagement of the piston |66 with the upper end of sleeve 88. Upward movement of piston |66 and tube 66 is limited by engagement of the piston |66 with a second sleeve |64 threaded into the lower end of a tubular member |66 whose upper end is threaded into the head 36. The tubular member |66 provides a shoulder |68 forming a support for a ring H6. This ring l|6 constitutes the abutment for a spring ||2 which compresses packing rings ||4 between washer ||6 and the upper end of sleeve |64 to prevent leakage of lubricant between the tube 66 and tubular member |66.

This tubular member |66 provides an upper pumping chamber H8. The upper end of the pumping chamber ||8 communicates through f port |26 with a booster chamber |22 containing a tubular piston |24 having a check valve |26 preventing reverse flow of lubricant therethrough. A stationary tubular member |28 is in telescopic engagement with the piston |24 and a spring pressed check valve |36 controls communication between the interior of this tubular member and the lubricant discharge conduit 46.

This same check valve |36 also controls communication between the interior of tubular member |28 and a passage |32 formed in the head 36 and communicating with a pipe |34 leading to the valve casting 32 whereby the lubricantpressure in the lubricant discharge conduit is communicated to the lubricant pressure operated valve means which controls the bypass for the primary fluid. 'The tubular member |28 is held in place by a threaded plug |36 which also forms an abutment for the spring |38 of the check valve |36.

A single acting piston |46 is attached to the upper end of the tube 66 by a neck |42 having ports |44 which provide communication between the interior of the tube 66 and the upper pumping chamber H8. This single acting piston |46 slides in a cylinder |46 whose upper end is threaded into the head 36. As best shown in Fig. 7, the upper end of cylinder |46 is connected by bores |48 and |56 with a primary fluid pipe |52 leading to the valve block 32. A third bore |54 connects this same primary uid pipe |52 with the annular passage |56 formed between the cylinder |62 and tubular member |66 and serving to admit primary iluid to the upper side of the double acting piston |66.

Primary fluid is admitted to the lower side of the double acting piston lili) by way of annular passage |59 formed between cylinder m2 and Sleeve 52, bo-re l and pipe itil connecting head 3b with valve block 32. Primary nuid pipe 16) is also connected to the upper end of the booster chamber |22 by way of bores E52 and Mill. When the valve mechanisms are in the position shown in Fig. l and the parts of the lubricant compressor are in the position shown in Figs. 4 and 4A, primary fluid delivered by pump 22 nows through pipe 28 and port 3Q into the righthand end of the valve chamber itt of the lubricant pressure operated bypass valve 68.

The primary fluid ows freely through this valve chamber into passage iil, around the reduced portion of the reversing valve i12, through bore lili, pipe it, bore 56 and annular passage 55 to the lower side of the piston lil. A feature of my invention lies in the fact that the primary iiuid pump 22 develops only a nominal pressure such as 500 pounds per square inch, so that the piping connections for the primary uid can be made of relatively inexpensive material and by relatively inexpensive manufacturing methods.

The force exerted by the primary fluid on the lower end of piston iii@ causes this piston and tube Se attached thereto to move upwardly, the cylinder EQ2 above the piston itt being evacuated for this purpose through the annular passage i555, the bore 15d, the pipe l52, bores 252, 22S and 23d in the casting 32, and a pipe ilii leading to the reservoir 26. This upward movement oi the tube (it carries with it the piston ifi@ and rod dll and since the piston ifi@ has a cross section larger than the tube ES, the lubricant capacity of chamber l i8 is increased by this upward movement.

The lubricant capacity of chamber Sd is also increased since tube 65 has a greater cross section than rod Gli. As tube 65 is common to both pumping chambers, the effective enlargement of these chambers is represented by the difference in cross section between the rod E@ and the piston Util. Lubricant can fio-w upwardly through tube from the lower pumping chamber to the upper pumping chamber and as this tube and rod 66 move upwardly, feeder 32 forces additional lubricant past valve SQ into the lower pumping chamber 84.

When piston li engages the lower end of stationary sleeve tibi, the piston can move no farther and the pressure in the primary iiuid line between this piston and the pump 22 builds up to a maximum. This primary uid line is connected by a bore H6 in the casting 32 (Fig. 1) with the righthand side of a piston H3 attached to the reversing valve V52. Just before this primary fluid pressure reaches the maximum which the pump 22 is capable of delivering, the force exerted by the primary fluid on the piston lill shifts the valve H2 from the position shown in Fig. 1 to that shown in Fig. 3. In effecting this shift of the valve 512, the force exerted by the primary fluid on the piston il@ was suicient to overcome the resistance to movement of the valve offered by the rollers iisd and 482 mounted, respectively, on the ends of pivoted arms iSd and 86 and urged by a spring 83 into engagement with the end groove i953 in a spool H92 attached to the end o-f the valve stem itil. In this movement of the piston |18, the oil immediately to the left of the piston is forced out through a bore 2911i in the casting 32 and the communicating bores 2%32 and 23S which open into said pipe 2Gb leading to the reservoir 26. After the reversing valve has shifted to the position shown in Fig. 3,

6 the rollers IBB and l82 engage a second groove H in the spool |92 and tend to hold the valve inthe position shown in this figure.

When the reversing valve H2 is in the position shown in Fig. 3, the primary fluid pipe i60 which communicates with the lower end of the double acting piston lite is connected by way of bores l'M and ist in the casting 32 to a primary fluid return pipe 255 leading to the'reservoir 26. At the same time, in the changed positions of the parts, primary iiuid from the pump 22 flows rough pipe 23, port Sil, valve chamber ISS, bore l'l, around the reduced portion of reversing valve H2, through bore 2ll2 and pipe |52 to head 3ft. Here part of the primary fluid flows through bor-es l5@ and IAS to the upper side of single act'- ing piston Mii. The remainder of the primary fluid ows through bore i511 and annular passage ltil tothe upper end of the double acting piston itil.

The primary fluid acting on the upper ends of pistons lil@ and llill causes these pistons and tube S5 to move downwardly, thereby displacing lubricant from both pumping chambers 84 and H8. The lubricant displaced from the lower chamber flows upwardly through the tube 65 and passes through ports lll@ into the upper chamber. The combined lubricant discharge from both chambers ows through port E20 into that part of booster chamber 22 which is below the upper end of tubular piston 12d. The upper end of the booster chamber is connected by bores |64 and ltr to pipe It@ which, in turn, is connected.

through the valve block 32 with the return pipe leading to the reservoir 2G.

The lubricant discharged into the booster chamber from the pumping chambers can now freely past the check valve 62% in the booster piston, kbut passage of this lubricant into the discharge conduit [5G is opposed by the spring pressed check valve ist and by any pressure existing in the discharge conduit. If this pressure in opposition to the ow of the lubricant is not more than about 3,000 pounds per square inch, the lubricant is forced outwardly through the conduit di? with little or no movement of the booster piston 924i. if, however, the pressure in opposition to the lubricant exceeds the pressure developed by the pistons me and Mt, the booster piston moves upwardly, thereby closing check valve 216 and forcing lubricant past the check valve ist under a pressure several times greater than the pressure of the lubricant discharged from the pumping cylinders. The parts of the booster and pumping mechanisms may be given any desired dimensions so that the lubricant discharged may attain a pressure many times that of the primary iluid. lThe particular apparatus illustrated in Figs. 1 to 7 of the drawings is designed to deliver lubricant under a maximum pressure of approximately 8,000 pounds per square inch with a primary uid pressure of 500 pounds per square inch, giving a pressure multi# plication of 16 to 1.

As will be readily understood, the reason why the booster piston E24 is eective for producing increased pressure is that the entire bottom face of the piston is subjected to the pressure of the grease in the chamber l22, whereas this pressure is transmitted to the grease over an area of substantially smaller size. It is clear also that during the upward movement of the booster piston E24, the downward movement of the pistons |00 and lili] and the tube GS is very substantially slowed down, such retarded movement continuing until the abnormal opposition to the movement of the grease has been overcome.

The movement of the booster piston |24 upwardly during the downward movement of the pistons and |40 in their power strokes is permitted by reason of the fact that during such downward movement of the pistons |00 and |40, with the valve |12 in the valve head 32 in the position shown in Fig. 3, the space about the tubular member |26 above the piston |24 is connected by the bores |64 and |62: with the pipe |60 for the escape of the oil from such space to the reservoir 26.

When the piston |00 engages the lower stationary sleeve 88, further movement of this piston and its associated parts is prevented and the pressure in the primary fluid line connecting the upper side of this piston and the upper side of the piston |40 with the pump 22 increases. This pressure is communicated to the lefthand side of the reversing valve piston |`|8`by way of a duct 204 and just before this pressure reaches the maximum which the pump 22 can create, valve |12 is shifted back to the position shown in Fig. l. This reverses the direction of flow of the primary fluid in the pipesI |52 and |60 and initiates another upward or suction stroke of the pumping mechanism. At the same time primary fluid is delivered to the upper side of the booster piston |24 by way of bores |62 and |64, thereby returning this booster piston to the lower position shown in Fig. 4.

In the normal use of my novel lubricating system, the pump 22 operates continuously and the pumping mechanism continues to operate the pistons |00 and |40 until the pressure in the lubricant discharge conduit 46 attains a predetermined maximum which operates the primary iiuid bypass valve |68, as when the control valve 48 of the conduit 46 is closed. Passage |32 in head 36 and pipe |34 transmit the lubricant pressure in the discharge conduit 46 to a duct 206 leading tothe cylinder 208 containing a piston 2 0 attached to the valve |63. During the operation of the pumping mechanism the valve |68 is held in the position shown in Fig. l by the force of a spring 2|2 and the resistance of the rollers 2|4 and 2|6 mounted, respectively, on pivoted arms 2|8 and 220 and urged by a spring 222 into engagement with the righthand groove 224 in a spool 226.

When the lubricant pressure in the discharge conduit attains a predetermined maximum, which happens in every instance when the control valve 48 is closed, piston 'llt moves valve |68 to the position shown in Fig. 2 and in this position the primary fluid delivery through pipe 28 to port 30 ilows around the reduced portion of valve 68 and through bores 226 and 230 to the return pipe 200 leading back to the reservoir 26. This releases all primary uid pressure on the pump pistons |00 and |40 and on the booster piston |24 so that these pistons come to rest while the pump 22 continues to operate. As soon as the pressure in the lubricant discharge conduit 46 drops, as by opening control valve 48, spring 2| 2 returns valve |66 to the position shown in Fig. 1 and operation of the pumping mechanism is resumed.

From the foregoing description, it will be apparent that in Figs. l to 7, inclusive, of the drawings I have shown a lubricating system having a single acting pumping mechanism or lubricant compressor provided with an automatic booster which comes into action when necessary, and

-wherein the power operated pump delivers pri- 8 mary uid ordinarily at a relatively low pressure, although the lubricant can be delivered to the bearing at a substantially higher pressure by the automatic action of the booster when necessary. The connections between the power driven pump and the lubricant compressor can accordingly be made of inexpensive parts formed of inexpensive materials by conventional manufacturing processes and machinery. High pressure is limited to a comparatively small proportion of the parts which may be made of higher grade materials.

In Figs. 8, 9 and l0, I have shown a modified form of my invention utilizing a somewhat different lubricant compressor which is not provided with' a booster mechanism. This compressor has the same lower structure as the compressor of the previous embodiment so that Fig. 4A is common to both forms of my invention as are also Figs. l, 2 and 3. In addition to eliminating the booster, the embodiment of Fig. 8 dii"- fers from that of Fig. 4 principally in that the compressor of Fig. 8 discharges lubricant on both strokes of the pumping mechanism, whereas the embodiment of Fig. 4 discharges lubricant only on one stroke.

Referring to Fig. 8, it will be seen that the piston |46 attached to the upper end of the tube 66 is of smaller diameter than the tube 66 so that upward movement of this piston and tube discharges lubricant from the upper pumping chamber H8' through' port 250 into lubricant discharge conduit 46. Check valve i6 in the housing 16 attached to the lower end of the tube 66 prevents reverse ow of lubricant through this tube 66 from the upper to the lower pumping chambers. During the upward stroke of the tube 66, lubricant is forced into the lower pumping chamber 84 as in the previous embodiment and during the following down stroke lubricant from the lower pumping chamber is forced through tube 66 through the upper pumping chamber where it enters by way of ports |44. The quantity of lubricant discharged by the lower pumping chamber during the downward stroke of the tube 66 is more than sufcient to satisfy the increasing capacity of the upper pumping chamber H8' so that some lubricant is Ydischarged through port 256 into discharge hose 46 during the downward stroke of the tube 66.

While the compressor of Fig. 8 discharges lubricant on both strokes, the total quantity discharged for a complete cycle is the difference in diameter between the rod 64 and piston |40 multiplied by the length of stroke. As the piston |46 is of smaller diameter than the piston |40, the quantity of lubricant discharged by the compressor of Fig. 8 for a given length of stroke is less than that discharged by the compressor of Fig. 4.

On the other hand, the pumping chambers 84 and ||8' of the modified compressor of Fig. 8 are capable of discharging lubricant at higher pressures than the pumping chambers 84 and ||8 of Fig. 4, so that the compressor of Fig. 8 requires no booster. .The structure of Fig. 8 is particularly advantageous where only moderate pressures are required, although this compressor can be designed to provide any desired pressure by varying the dimensions of the essential parts of the pumping mechanism.

While I have shown and described only two embodiments of my invention, it is to be understood that my invention may assume numerous other forms and includes all modifications and variations coming within the scope of the appended claims.

I claim:

1. A lubricating system, comprising a primary pump for supplying primary fluid at relatively low pressure, a lubricantl compressor comprising a part movable by said primary fluid alternatively in opposite directions for forcing lubricant from said compressor, a reversing valve mechanism interposed in the connections between said primary pump and sai-.d lubricant compressor for shifting the pressure of said primary fluid from one side of said'movablepart to the other side, a discharge conduit for said lubricant compressor, a conltrol valve for regulating discharge of lu-i bricant through said conduit, and a bypass valve for said primary fluid responsive directly to pressure variations in said discharge conduit for relieving the pressure of said primary fluid on said I.movable part.

2. A lubricating system of the class described, comprising a primary fluid reservoir, a pump supplied from said reservoir, a motor for driving said pump, a valve block, a conduit connecting said pump and valve block, a second conduit connecting said valve block and reservoir, a bypass valve in said valve block for establishing communication between said conduits for idling operation of said pump, a lubricant compressor comprising a part movable by said primary uid alternatively in opposite directions for forcing lubricant from said. compressor, a pair of conduits connecting said valve block withl said compressor, reversing valve mechanism. in said valve block for alternately connecting each'of said last-named conduits with each ofsaid first-named conduits for shifting the pressure of said primary fluid from one side of said movable part to the other side, a lubricant discharged conduit for said compressor, and means responsive to pressure variations in said discharge conduit for shifting said bypass valve and adapted when. a. predetermined maximum; pressurey is reachedto move the bypass valve to position. for causingI the pump to idle.

3. A lubricating system of the class described, comprising a primary fluid pump, a lubricant compressor operated by primary uid discharged from said pump, said compressor having piston means therein, conduit connections between said compressor and pump for supplying primary uid to opposite sides of said piston means, an automatic reversing valve for reversing the direction of application of primary fluid to said piston means for forcing lubricant froml the compressor, and automatic booster means in said compressor adapted substantially to increase the pressure applied upon the lubricant when necessary for overcoming the resistance to the flow of the lui bricant from the compressor.

4. A lubricating system of thev class described, comprising a primary fluid pump, a lubricant compressor operated by primaryl fluid discharged fromy said pump, said compressor having piston means therein, conduit connections between said compressor and pump for supplying primary fluid to opposite sides of said piston means, an automatic reversing valve for reserving the direction of application of primary fluid to said piston means for forcing lubricant from the compressor, a booster for said compressor for increasing the pressure applied on the lubricant for ejecting it, and means for conducting primary fluid to one side of said booster for returning it to normal position after an operative stroke.

5. A lubricating system, comprising a lubricant compressor having a pair of pumping chambers, means extending into said pumping chambers for displacing lubricant therefrom, said means providing a lubricant conduit from one pumping chamber to the other, a. cylinder intermediate said pumping chambers, packing glands between said cylinder and said pumping chambers, a piston in said cylinder for reciprocating said lubricant-l displacing means, a pump for supplying primary fluid alternatively at opposite sides of the piston for operating the piston in either direction, and an automatic reversing valve for shifting the application of the primary fluid from one side of the piston to the other.

6. A lubricatingk systemV of the class described, comprising a compressor having a pair of lubricant pumping chambers, means extending into said pumping chambers for displacing lubricant therefrom, said means providing a conduit for lubricant from one pumping chamber to the other, a cylinder intermediate said pumping chambers, a piston in said cylinder for reciprocating said means, a pump for delivering primary fluidto operate said piston in both directions, a motor for driving said primary fluid pump, conduits connecting said pump with opposite ends Iof said cylinder, and an automatic reversing valve controlling the application of primary fluid to said piston.

'7. A lubricating system of. the class described, comprising a compressor having a pair of 1ubricant pumping chambers, means extending into said pumping chambers for displacing lubricant therefrom, said means providing av conduit for lubricant from one pumping chamber to the other, a cylinder intermediatel said pumping chambers, a piston in said cylinder for reciprocating said means, a pumpfor delivering primary fluid to operate said piston in both directions, a motor for driving said primary fluid pump, conduits connecting said pump with' opposite ends of said cylinder, an. automatic reversing Valve controlling the application of primary fluid to said piston, a lubricant discharge conduit for said compressor, and means responsive to pressure in said discharge conduit for rendering said primary pump ineffective -to operate said piston,

8. A lubricating system of the class described, comprising a compressor having a pair of 1ubricant pumping chambers, means extending into said pumping chambers for displacing lubricant therefrom, said means providing a conduit for lubricant from one pumping chamber to the other, a cylinder intermediate said pumping chambers, a piston in said cylinder for reciprocating said means, a pump for delivering primary uid to operate said piston in both directions, a motor for driving said primary fluid pump, conduits connecting said pump with opposite ends of said cylinder, an automaticl reversing valve controlling the application of primary fluid to said piston, a lubricant discharge conduit for said compressor, means responsive to pressure in said discharge conduit for rendering said primary pump ineffective to operate said piston, and a booster in said compressor adapted when the resistance in the discharge conduit reaches a predetermined maximum to come into action for substantially increasing the pressure on the lubricant for ejecting it.

9. A compressor of the class described, comprising a head, a rst pumping chamber, a second pumping chamber, means extending into said pumping chambers for displacing material therefrom, means providing a lubricant conduit from one pumping chamber to the other, a cylinder intermediate said pumping chambers, a piston in said cylinder for reciprocating said means, and

a booster movably mounted in said head and subject to the pressure of the material displaced from said pumping chambers over a selected area and transmitting such' pressure to the material over a substantially smaller area for increasing the pressure for ejecting the material from the head.

10. A lubricating system of the type described, comprising in combination'a pump, a lubricant compressor connected with said pump for operation by a stream of primary iiuid driven by said pump so as to force a stream of lubricant through the compressor, a discharge conduit through which the lubricant is discharged from the compressor, a control valve for regulating the discharge of lubricant through the conduit, and

means comprising a by-pass valve responsive to pressure variations in said discharge conduit and adapted When the pressure on the lubricant in said conduit reaches a predetermined maximum to shift the connections for` diverting from the compressor the stream of primary fluid coming from the pump and for relieving almost completely the pressure on the primary iiuid passing through the pump.

1l. A lubricating system of the type described,

comprising in combination a pump, a lubricantf compressor connected with said pump for operation by a stream of primary huid driven by said pump so as to force a stream of lubricant through the compressor, a discharge conduit through which the lubricant is discharged from the com-- presser, a control valve for regulating the dis charge of lubricant through` the conduit, Ymeans comprising a bypass valve responsive to pressure Variations in said discharge conduit and adapted when the pressure on the lubricant in said conduit reaches a predetermined maximum to shift the connections for diverting from the compressor the stream of primary fluid coming from the pump and relieving almost completely the pressure on the primary fluid passing through the pump, and yielding means adapted normally to hold said by-pass valve releasably in position for diverting the primary fluid from the compressor.

12. A lubricating system of the type described, comprising in combination a pump, a lubricant compressor connected with said pump for operation by a stream of primary iluid driven by said pump so as to force a stream of lubricant through the compressor, a discharge conduit through which the lubricant isdischarged from the compressor, a control valve for regulating the discharge of lubricant through the conduit, means comprising a by-pass valve responsive to pressure variations in said discharge conduit and adapted when the pressure on the lubricant in said conduit reaches a predetermined maximum to shift the connections for diverting from the compressor the stream of primary uid coming from the pump and for relieving almost completely the pressure on the primary fluid passing through the pump, a spring normally opposing movement of the control parts into position for diverting the primary lluid from the compressor, and spring operated resistance means adapted normally to hold said control parts releasably from movement either into er out of position for causing the diversion of the primary fluid from the compresser.

13. A lubricating system of the class described, comprising a primary fluid pump, a lubricant compressor having piston means therein, means connecting said pump to said compressor for movement of said piston means in both directions by the pressure of the primary fluid discharged from the pump and comprising conduits leading from the pressure supplying discharge of the pump to opposite sides respectively of the piston means, and an automatic reversing valve actuated by the increased pressure in one of said conduits when the piston means has traveled to the limit of its motion in one direction to shift the pressure supplying connection of the pump to the other conduit and actuated in turn by the increased pressure in said other conduit when the piston means has traveled to the limit of its motion in the opposite direction to shift the pressure supplying connection of the pump back to said one conduit.

14. A lubricating system of the class described, comprising a primary fluid pump, a, lubricant compressor having piston means therein, means connecting said pump to said compressor for movement of said piston means by th'e primary fluid discharged from the pump and comprising conduits leading from the pressure supplying discharge of the pump to opposite sides respectively of the piston means, an automatic reversing valve actuated by the pressure in said conduits adapted 'when the pressure in the active conduit builds up to a predetermined maximum to shift the pressure supplying connection of the pump to the other conduit, and resistance means connected with said reversing valve adapted yieldingly to resist the movement of said valve for shifting th'e connection from either of the conduits to the other.

GEO. 1-1. PALM.

' REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 2,276,358 Vickers Mar. 17, 1942 2,022,232 Davis Nov. 26, 1935 2,289,567 Berglund July 14, 1943 1,722,412 Eisenhauer July 30, 1929 278,018 Hudson May 22, 1883 2,312,857 Woelfer Mar. 2, 1943 2,056,204 Noack Oct. 6, 1936 1,816,157 Scott July 28, 1931 2,287,709 Ringman June 23, 1942 2,217,880 Woodson Oct. 15, 1940 1,770,912 Clapp July 22, 1930 2,240,901 Ferris May 6, 1941 2,380,608 Palm July 31, 1945 

